JPH03350A - V-belt type continuously variable transmission - Google Patents

V-belt type continuously variable transmission

Info

Publication number
JPH03350A
JPH03350A JP1132025A JP13202589A JPH03350A JP H03350 A JPH03350 A JP H03350A JP 1132025 A JP1132025 A JP 1132025A JP 13202589 A JP13202589 A JP 13202589A JP H03350 A JPH03350 A JP H03350A
Authority
JP
Japan
Prior art keywords
sheave
input
belt
continuously variable
variable transmission
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP1132025A
Other languages
Japanese (ja)
Other versions
JP2558522B2 (en
Inventor
Mitsunao Takayama
高山　光直
Tsutomu Yasue
安江　勉
Akiyoshi Morishita
森下　秋吉
Kozo Yamauchi
山内　鉱三
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aichi Machine Industry Co Ltd
Original Assignee
Aichi Machine Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP1132025A priority Critical patent/JP2558522B2/en
Application filed by Aichi Machine Industry Co Ltd filed Critical Aichi Machine Industry Co Ltd
Priority to JP1132024A priority patent/JPH03358A/en
Priority to DE89306451T priority patent/DE68910680T2/en
Priority to ES89306451T priority patent/ES2048288T3/en
Priority to EP89306450A priority patent/EP0405021B1/en
Priority to ES89306450T priority patent/ES2052005T3/en
Priority to EP89306451A priority patent/EP0405022B1/en
Priority to AU37042/89A priority patent/AU627198B2/en
Priority to AU37043/89A priority patent/AU630098B2/en
Priority to US07/378,085 priority patent/US5050457A/en
Priority to US07/378,084 priority patent/US4964841A/en
Priority to CA002005074A priority patent/CA2005074C/en
Priority to CA002005075A priority patent/CA2005075C/en
Publication of JPH03350A publication Critical patent/JPH03350A/en
Application granted granted Critical
Publication of JP2558522B2 publication Critical patent/JP2558522B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66254—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
    • F16H61/66259—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using electrical or electronical sensing or control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/062—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions electric or electro-mechanical actuating means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19019—Plural power paths from prime mover

Abstract

PURPOSE:To improve the life of an actuator related member, reduce driving torque, and smoothly regulate transmission gear ratio by providing a spring energizing an input sheave on the movable side in the opposite direction to the axial force by a V-belt. CONSTITUTION:A roller holder 76 is fixed to an input sheave shaft 18 in the hollow cylinder part 40a of an input movable sheave 40 provided on the input sheave shaft 18 in such a manner as to be capable of sliding, and a compression coil spring 84 is interposed between the input sheave shaft and the inner surface of a conical part 40b. Thus, the axial force added to the input movable sheave 40 by a V-belt 60 is reduced by the compression coil spring 84, whereby the life of an actuator related member can be improved, driving torque can be reduced, and the transmission gear ratio can be smoothly regulated.

Description

【発明の詳細な説明】 （産業上の利用分野） この発明は、Ｖベルト式無段変速機に関する。[Detailed description of the invention] (Industrial application field) The present invention relates to a V-belt continuously variable transmission.

（従来技術） 従来、この種のＶベルト式無段変速機は第４図に示すよ
うに、入力シーブ軸Ａに取り付けられた一対の入力シー
ブＢ、Ｃのうちの一方の入力シーブＢを入力シーブ軸Ａ
に対し軸方向に可動とし、入力シーブＢの位置を図示し
ないアクチュエータにより駆動される入力シーブ位置調
節装置りにより調節するように構成されている。(Prior Art) Conventionally, this type of V-belt type continuously variable transmission inputs input sheave B, one of a pair of input sheaves B and C attached to input sheave shaft A, as shown in Fig. 4. Sheave shaft A
The input sheave B is movable in the axial direction, and the position of the input sheave B is adjusted by an input sheave position adjustment device driven by an actuator (not shown).

入力シーブ位置調節装置りは上記アクチュエータにより
回転駆動されるアウタスライダＥと該アウタスライダＥ
と螺合するインナスライダＦとを有しており、アウタス
ライダＥには入力シーブＢの後部がベアリングＧを介し
て支持され、かつ軸方向を係止されている。このためア
ウタスライダＥはアクチュエータ駆動により前後方向に
移動し、それに伴って可動側の入力シーブＢが移動して
位置調節が行なわれる。The input sheave position adjustment device includes an outer slider E rotated by the actuator and the outer slider E.
The rear part of the input sheave B is supported by the outer slider E via a bearing G, and is locked in the axial direction. Therefore, the outer slider E is moved in the front-rear direction by driving the actuator, and the input sheave B on the movable side moves accordingly to adjust the position.

（発明が解決しようとする課題） しかしながら、上記従来のＶベルト式無段変速機では、
運転時におけるＶベルトＨによる軸方向負荷がベアリン
グＧ、アウタスライダＥ等のアクチュエータの駆動力伝
達部材に直接加わるため、これらの部材（例えばベアリ
ングＧ）が損傷したり、アクチュエータに大きな駆動力
が必要となる欠点を有していた。(Problem to be solved by the invention) However, in the conventional V-belt type continuously variable transmission,
During operation, the axial load from the V-belt H is applied directly to the drive force transmission members of the actuator, such as the bearing G and outer slider E, which may damage these members (e.g. bearing G) or require a large drive force to the actuator. It had the following drawbacks.

（課題を解決するための手段） 上記従来技術の課題を解決するため、本発明のＶベルト
式無段変速機は、入力シーブ軸に取り付けられた離接可
能な一対の入力シーブと出力シーブ軸に取り付けられた
一対の出力シーブ間に巻掛けられたＶベルトを介し入力
シーブ軸の回転を前記出力シーブ軸に伝達可能に構成し
、かつ前記入力シーブのうちの可動側のλカシーブ位置
を調節するためにアクチュエータにより駆動されるシー
ブ位置調節装置を備えたＶベルト式無段変速機において
、前記可動側の入力シーブを前記Ｖベルトにより加えら
れる軸方向力と反対の方向に付勢するスプリングを設け
た構成とされる。(Means for Solving the Problems) In order to solve the problems of the prior art described above, the V-belt type continuously variable transmission of the present invention has a pair of input sheave and output sheave shaft that are attached to an input sheave shaft and can be separated from each other. The rotation of the input sheave shaft can be transmitted to the output sheave shaft via a V-belt wrapped between a pair of output sheaves attached to the output sheave, and the position of the movable λ sheave of the input sheaves is adjusted. In a V-belt type continuously variable transmission equipped with a sheave position adjustment device driven by an actuator in order to It is assumed that the configuration is as follows.

（作用） 本発明のＶベルト式無段変速機ではＶベルトにより可動
側の入力シーブに加わる軸方向力がスプリングによって
相殺されるため、シーブ位置調節装置のアクチュエータ
関連部材に加わる負荷が軽減される。(Function) In the V-belt type continuously variable transmission of the present invention, the axial force applied to the input sheave on the movable side by the V-belt is offset by the spring, so the load applied to the actuator-related members of the sheave position adjustment device is reduced. .

（実施例） 次に、この発明の一実施例を添付の図面を参照して説明
する。(Example) Next, an example of the present invention will be described with reference to the accompanying drawings.

第１図において、入力シーブ＃＋１８の前部には該入力
シーブ軸１８に固定された入力固定シーブ３８と、入力
シーブ軸１８に対し軸方向に摺動可能に取り付けられた
入力可動シーブ４０と、この人力可働シーブ４０の軸方
向位置を調節するためのシーブ位置調節装置４２が設け
られている。In FIG. 1, the front part of input sheave #+18 includes an input fixed sheave 38 fixed to the input sheave shaft 18, and an input movable sheave 40 mounted so as to be slidable in the axial direction with respect to the input sheave shaft 18. A sheave position adjustment device 42 is provided for adjusting the axial position of this manually movable sheave 40.

一方、入力シーブ軸１８の側部には該入力シーブ軸１８
と平行に出力シーブ軸４４が配置されており、出力シー
ブ軸４４には該出力シーブ軸４４に固定された出力固定
シーブ４６と、出力シーブ軸４４に対し軸方向に摺動可
能に取り付けられた出力可動シーブ４８とが設けられて
いる。On the other hand, on the side of the input sheave shaft 18, the input sheave shaft 18 is
An output sheave shaft 44 is arranged parallel to the output sheave shaft 44, and an output fixed sheave 46 is fixed to the output sheave shaft 44, and an output sheave shaft 46 is attached to the output sheave shaft 44 so as to be slidable in the axial direction with respect to the output sheave shaft 44. An output movable sheave 48 is provided.

上記入力固定シーブ３Ｂと入力可動シーブ４０は対面す
る側が円錐面状を成して、相互間にＶ字溝５０を形成し
、両者で入力シーブ５２を構成している。同様に、出力
固定シーブ４６と出力可動シーブ４８は対面する側が円
錐面状を成して、相互間にＶ字溝５６を形成し、両者で
出力シーブ５８を構成している。入力シーブ５２と出力
シーブ５８との間にはＶベルト６０が巻掛けられており
、上記シーブ位置調節装置４２により入力可動シーブ４
０の位置を調節することにより、Ｖ字溝５０の幅を変え
ることで入力シーブ軸１８の回転に対する出力シーブ軸
４４の回転の変速比を無段に可変となっている。The input fixed sheave 3B and input movable sheave 40 have conical surfaces facing each other, form a V-shaped groove 50 therebetween, and together constitute an input sheave 52. Similarly, the output fixed sheave 46 and the output movable sheave 48 have conical surfaces facing each other, and form a V-shaped groove 56 therebetween, and together constitute an output sheave 58. A V-belt 60 is wound between the input sheave 52 and the output sheave 58, and the input movable sheave 4 is adjusted by the sheave position adjustment device 42.
By adjusting the 0 position and changing the width of the V-shaped groove 50, the speed ratio of the rotation of the output sheave shaft 44 to the rotation of the input sheave shaft 18 can be made infinitely variable.

次に、上記シーブ位置調節装置４２の構成を詳しく説明
する。Next, the configuration of the sheave position adjustment device 42 will be explained in detail.

入力シーブ軸１Ｂの前端には軸受６２が取り付けられて
おり、この軸受６２には雄ネジ筒部６６ａを一体で有す
る筒状のインナスライダ６６が支承されている。インナ
スライダ６６は入力可動シーブ４０の前部を取り囲む（
図は一部のみを示す）ケース６Ｂにビン７０を介して固
定されており、ケース６Ｂは図示しない固定部に取り付
けられている。インナスライダ６６の雄ネジ筒部６６ａ
は入力シーブ軸１８に対し適宜隙間を隔ててその軸方向
に延在しており、図示しないアクチュエータにより正逆
回転駆動されるアウタスライダ７２の雌ネジ筒部７２ａ
と螺合している。A bearing 62 is attached to the front end of the input sheave shaft 1B, and a cylindrical inner slider 66 integrally having a male threaded cylindrical portion 66a is supported on this bearing 62. The inner slider 66 surrounds the front part of the input movable sheave 40 (
It is fixed to a case 6B (only a part of which is shown) via a bottle 70, and the case 6B is attached to a fixing part (not shown). Male threaded cylinder portion 66a of inner slider 66
Extends in the axial direction of the input sheave shaft 18 with an appropriate gap therebetween, and is a female threaded cylindrical portion 72a of the outer slider 72 that is driven to rotate in forward and reverse directions by an actuator (not shown).
It is screwed together.

一方、入力可動シーブ４０の前部には中空筒部４０ａが
一体形成されており、この中空筒部４０ａは上記アウタ
スライダ７２の雌ネジ筒部７２ａに対し軸受７４を介し
て相対回転可能かつ軸方向に追従動可能に取り付けられ
ている。On the other hand, a hollow cylinder part 40a is integrally formed in the front part of the input movable sheave 40, and this hollow cylinder part 40a is rotatable relative to the internally threaded cylinder part 72a of the outer slider 72 via a bearing 74, and It is attached so that it can follow the direction.

又、入力シーブ軸１８には、入力可動シーブ４０の中空
筒部４Ｏａ内において環状のローラホルダー７６がＣリ
ング７８により固定されている。Further, an annular roller holder 76 is fixed to the input sheave shaft 18 within the hollow cylinder portion 4Oa of the input movable sheave 40 by a C ring 78.

ローラホルダー７６の一部には半径方向外方へ突部７６
ａが形成されており、この突部７６ａは上記中空筒部４
０ａの内周面に形成された軸方向−対の突条８０．８０
（第３図参照）間に突出している。又、突部７６ａには
突条８０．８０の相対する内面に当接するローラベアリ
ング８２が取り付けられており、入力可動シーブ４０の
軸方向への案内機構を構成している。A portion of the roller holder 76 has a radially outward protrusion 76.
a is formed, and this protrusion 76a is connected to the hollow cylindrical portion 4.
Axial pair of protrusions 80.80 formed on the inner peripheral surface of 0a
(See Figure 3) It protrudes between the two. Furthermore, a roller bearing 82 is attached to the protrusion 76a, which abuts on the opposing inner surfaces of the protrusions 80, 80, and constitutes a guide mechanism for the input movable sheave 40 in the axial direction.

さらに、入力可動シーブ４０の中空筒部４０ａ内には円
錐部４０ｂの内面とローラホルダー７６との間において
圧縮コイルスプリング８４が介在されており、入力可動
シーブ４０は圧縮コイルスプリング８４により入力固定
シーブ３８側への付勢力が加えられている。Furthermore, a compression coil spring 84 is interposed in the hollow cylindrical portion 40a of the input movable sheave 40 between the inner surface of the conical portion 40b and the roller holder 76, and the input movable sheave 40 is connected to the input fixed sheave by the compression coil spring 84. A biasing force is applied to the 38 side.

シーブ位置調節装置４２は上記構成により、アウタスラ
イダ７２をアクチュエータにより一方向に回転させると
、入力可動シーブ４０が突条８０．８０とローラホルダ
７６の突部７６ａにより案内されて、入力固定シーブ３
８偏に軸方向に動いてＶ字溝５０の幅を狭め、逆方向に
回転させると入力固定シーブ３８から遠ざかる方向に動
いてＶ字溝５０の幅を広げる。又、入力可動シーブ４０
は突条８０．８０と突部７６ａの係合により大力シーブ
軸１８に追従して回転可能となっている。With the above configuration, the sheave position adjusting device 42 has the above-mentioned configuration. When the outer slider 72 is rotated in one direction by the actuator, the input movable sheave 40 is guided by the protrusions 80, 80 and the protrusion 76a of the roller holder 76, and the input fixed sheave 3
When it is rotated in the opposite direction, it moves away from the input fixed sheave 38 and widens the width of the V-shaped groove 50. In addition, input movable sheave 40
is rotatable following the large force sheave shaft 18 by engagement between the protrusions 80 and 80 and the protrusion 76a.

本実施例のＶベルト式無段変速機において、入力可動シ
ーブ４０はＶベルト６０による出力シーブ５８への回転
伝達の際、常に軸方向前方、即ちＶ字溝５０が拡がる方
向の負荷を受け、この負荷はアウタスライダ７２による
中空筒部４０ａの前端の支持部に加わることとなる。し
かしながらこのような負荷は圧縮コイルスプリング８４
による付勢力により相殺されるためアウタスライダ７２
への負荷が軽減され、同様に軸受７４への負荷も軽減さ
れる。又、回転軸における入力可動シーブ４０の振動が
圧縮コイルスプリング８４によって吸収されるため駆動
時のノイズが低減する。In the V-belt type continuously variable transmission of this embodiment, when the input movable sheave 40 transmits rotation to the output sheave 58 by the V-belt 60, it always receives a load in the forward direction in the axial direction, that is, in the direction in which the V-shaped groove 50 widens. This load is applied to the support portion of the front end of the hollow cylinder portion 40a by the outer slider 72. However, such a load
The outer slider 72 is offset by the biasing force caused by the
The load on the bearing 74 is similarly reduced. Further, since the vibration of the input movable sheave 40 on the rotating shaft is absorbed by the compression coil spring 84, noise during driving is reduced.

従って、アウタスライダ７２はアクチュエータにより円
滑に回転駆動され、軸受７４も損傷を生じない。又、圧
縮コイルスプリング８４によって騒音防止効果をも得る
ことができる。Therefore, the outer slider 72 is rotated smoothly by the actuator, and the bearing 74 is not damaged. Further, the compression coil spring 84 can also provide a noise prevention effect.

第３区には変速比−人力可動シーブ４０への軸方向力（
驕）特性が従来例との比較で示してあり、図中曲線Ａは
本実施例の場合を、Ｂは従来例の場合を示す、尚、この
場合の圧縮コイルスプリング８４によるる荷重の変化は
図中曲線Ｃで示してあり、本実施例では従来例に比して
顕著な軸方向力低減効果が得られている。The third section shows the transmission ratio - the axial force on the manually operated sheave 40 (
The curve A in the figure shows the case of this embodiment, and the curve B shows the case of the conventional example. In this case, the change in the load due to the compression coil spring 84 is This is shown by curve C in the figure, and this embodiment has a remarkable axial force reduction effect compared to the conventional example.

（発明の効果） 本発明のＶベルト式無段変速機は、入力シーブ軸に取り
付けられた離接可能な一対の入力シーブと出力シーブ軸
に取り付けられた一対の出力シーブ間に巻掛けられたＶ
ベルトを介し入力シーブ軸の回転を前記出力シーブ軸に
伝達可能に構成し、かつ前記入力シーブのうちの可動側
の入力シーブ位置を調節するためにアクチュエータによ
り駆動されるシーブ位置調節装置を備えたＶベルト式無
段変速機において、前記可動側の入力シーブを前記Ｖベ
ルトにより加えられる軸方向力と反対の方向に付勢する
スプリングを設けたことにより、シーブ位置調節装置の
アクチュエータ関連部材に加わる可動側入力シーブから
の軸方向力を軽減できるので、アクチュエータ関連部材
の寿命が向上するとともにアクチュエータによる駆動ト
ルクを低減でき、変速比調節を円滑に行なえる利点を有
する。(Effects of the Invention) The V-belt type continuously variable transmission of the present invention has a V-belt type continuously variable transmission that is wound between a pair of separable input sheaves attached to an input sheave shaft and a pair of output sheaves attached to an output sheave shaft. V
The sheave position adjusting device is configured to be able to transmit the rotation of the input sheave shaft to the output sheave shaft via a belt, and is driven by an actuator to adjust the position of the input sheave on the movable side of the input sheaves. In the V-belt type continuously variable transmission, by providing a spring that biases the input sheave on the movable side in a direction opposite to the axial force applied by the V-belt, the spring is applied to actuator-related members of the sheave position adjustment device. Since the axial force from the input sheave on the movable side can be reduced, the life of the actuator-related members can be improved, and the driving torque by the actuator can be reduced, which has the advantage of making it possible to smoothly adjust the gear ratio.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図及び第２図は本発明の一実施例を示すもので、第
１図は一部を半断面で示したＶベルト式無段変速機の要
部の正面図、第２図は第１図の■−ｍ線断面図、第３図
は第１図及び第２図に示したＶベルト式無段変速機の変
速比−人力可動シーブへの軸方向性を従来例との比較で
示した図、第４図は従来のＶベルト式無段変速機の要部
の半断面正面図である。 １８・・・入力シーブ軸 ３８・・・入力固定シーブ ４０・・・入力可動シーブ ４２・・・シーブ位置調節装置 ４４・・・出力シーブ軸 ４６・・・出力固定シーブ ４８・・・出力可動シーブ ５２・・・大力シーブ ５８・・・出力シーブ ロ０・・・Ｖベルト ８４・・・圧縮コイルスプリング 特許出願人　　　　　　　愛知機械工業株式会社代理人
　　　弁理士　　　清　　水　　義　　久第 図 弔 図 弔 図 第 図Figures 1 and 2 show an embodiment of the present invention. Figure 1 is a front view of the main parts of a V-belt continuously variable transmission, partially shown in half cross section, and Figure 2 is a front view of the main parts of a V-belt continuously variable transmission. The sectional view taken along the ■-m line in Figure 1 and Figure 3 compare the gear ratio of the V-belt type continuously variable transmission shown in Figures 1 and 2 with the axial direction to the manually operated sheave. The figure shown in FIG. 4 is a half-sectional front view of the main parts of a conventional V-belt type continuously variable transmission. 18... Input sheave shaft 38... Input fixed sheave 40... Input movable sheave 42... Sheave position adjustment device 44... Output sheave shaft 46... Output fixed sheave 48... Output movable sheave 52...Power sheave 58...Output sheave 0...V belt 84...Compression coil spring Patent applicant Aichi Kikai Kogyo Co., Ltd. Agent Patent attorney Yoshi Shimizu

Claims (1)

【特許請求の範囲】[Claims] 入力シーブ軸に取り付けられた離接可能な一対の入力シ
ーブと出力シーブ軸に取り付けられた一対の出力シーブ
間に巻掛けられたＶベルトを介し入力シーブ軸の回転を
前記出力シーブ軸に伝達可能に構成し、かつ前記入力シ
ーブのうちの可動側の入力シーブ位置を調節するために
アクチュエータにより駆動されるシーブ位置調節装置を
備えたＶベルト式無段変速機において、前記可動側の入
力シーブを前記Ｖベルトにより加えられる軸方向力と反
対の方向に付勢するスプリングを設けたことを特徴とす
るＶベルト式無段変速機。The rotation of the input sheave shaft can be transmitted to the output sheave shaft via a V-belt wrapped between a pair of separable input sheaves attached to the input sheave shaft and a pair of output sheaves attached to the output sheave shaft. In the V-belt continuously variable transmission, the V-belt continuously variable transmission is configured to have a sheave position adjustment device driven by an actuator to adjust the position of the input sheave on the movable side of the input sheave, A V-belt type continuously variable transmission characterized in that a spring is provided that biases in a direction opposite to the axial force applied by the V-belt.
JP1132025A 1989-05-25 1989-05-25 V-belt type continuously variable transmission Expired - Fee Related JP2558522B2 (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
JP1132024A JPH03358A (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission
JP1132025A JP2558522B2 (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission
ES89306451T ES2048288T3 (en) 1989-05-25 1989-06-26 TRANSMISSION OF CONTINUOUS VARIATION.
EP89306450A EP0405021B1 (en) 1989-05-25 1989-06-26 Continuously variable transmission
ES89306450T ES2052005T3 (en) 1989-05-25 1989-06-26 CONTINUOUSLY VARIABLE TRANSMISSION.
EP89306451A EP0405022B1 (en) 1989-05-25 1989-06-26 Continuously variable transmission
DE89306451T DE68910680T2 (en) 1989-05-25 1989-06-26 Infinitely variable transmission.
AU37043/89A AU630098B2 (en) 1989-05-25 1989-06-27 Continuously variable transmission
AU37042/89A AU627198B2 (en) 1989-05-25 1989-06-27 Continuously variable transmission
US07/378,085 US5050457A (en) 1989-05-25 1989-07-11 Continuously variable transmission
US07/378,084 US4964841A (en) 1989-05-25 1989-07-11 Continuously variable transmission
CA002005074A CA2005074C (en) 1989-05-25 1989-12-11 Continuously variable transmission
CA002005075A CA2005075C (en) 1989-05-25 1989-12-11 Continuously variable transmission

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP1132025A JP2558522B2 (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission
JP1132024A JPH03358A (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission
EP89306451A EP0405022B1 (en) 1989-05-25 1989-06-26 Continuously variable transmission
US07/378,084 US4964841A (en) 1989-05-25 1989-07-11 Continuously variable transmission
CA002005075A CA2005075C (en) 1989-05-25 1989-12-11 Continuously variable transmission

Publications (2)

Publication Number Publication Date
JPH03350A true JPH03350A (en) 1991-01-07
JP2558522B2 JP2558522B2 (en) 1996-11-27

Family

ID=39952187

Family Applications (2)

Application Number Title Priority Date Filing Date
JP1132025A Expired - Fee Related JP2558522B2 (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission
JP1132024A Pending JPH03358A (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission

Family Applications After (1)

Application Number Title Priority Date Filing Date
JP1132024A Pending JPH03358A (en) 1989-05-25 1989-05-25 V-belt type continuously variable transmission

Country Status (7)

Country Link
US (2) US5050457A (en)
EP (2) EP0405022B1 (en)
JP (2) JP2558522B2 (en)
AU (2) AU630098B2 (en)
CA (2) CA2005075C (en)
DE (1) DE68910680T2 (en)
ES (2) ES2052005T3 (en)

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US8052561B2 (en) 2002-04-10 2011-11-08 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Method for optimizing plates of a plate link chain, and plate for a plate link chain

Also Published As

Publication number Publication date
EP0405022B1 (en) 1993-11-10
DE68910680T2 (en) 1994-03-03
CA2005074C (en) 1995-02-14
AU630098B2 (en) 1992-10-22
EP0405021A1 (en) 1991-01-02
JPH03358A (en) 1991-01-07
DE68910680D1 (en) 1993-12-16
ES2052005T3 (en) 1994-07-01
AU3704289A (en) 1991-01-03
JP2558522B2 (en) 1996-11-27
AU627198B2 (en) 1992-08-20
EP0405021B1 (en) 1994-03-02
AU3704389A (en) 1991-01-03
ES2048288T3 (en) 1994-03-16
CA2005075A1 (en) 1991-06-11
US4964841A (en) 1990-10-23
EP0405022A1 (en) 1991-01-02
US5050457A (en) 1991-09-24
CA2005074A1 (en) 1991-06-11
CA2005075C (en) 1995-07-18

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